Rotary drive linear rod displacement pump

ABSTRACT

A rotary drive linear rod displacement pump includes a pump housing supporting a plurality of radially spaced linear rod displacement pump segments. A rotor supporting a plurality of roller cam followers is rotatably coupled to the pump segments and is driven by a source of rotary power. As the rotor is driven, the cam followers articulate the pump segments.

FIELD OF THE INVENTION

This invention relates generally to pumps and particularly to thoseoperated in response to a rotary power drive source.

BACKGROUND OF THE INVENTION

Pumps comprise one of the most common well developed and well known typeof basic machines. The essential function of a pump is the displacementand movement or pressurization of a fluid. The majority of pumps may bedivided into a basic classification as either reciprocating or rotaryaction pumps. Reciprocating pumps typically utilize one or morecylinders together with appropriate valves for controlling fluid flow toand from the cylinders. Each cylinder within the reciprocating pump isfitted with a moving piston which in turn is coupled to a crankmechanism or the like for imparting piston movement within the cylinder.Most reciprocating pumps are coupled to a rotary, or linear drive powersource.

One of the oldest types of reciprocating pumps is often referred to inthe art as a “rod pump”. Rod pumps are characterized by providing use inhigh pressure or fluid metering applications. Typically rod pumpsutilize a fluid cylinder having a closed end bore within which a pumprod is moved. The open end of the fluid cylinder bore supports apressure seal against the pump rod for maintain pressure within thecylinder bore. Pumping is accomplished by initially drawing the rod fromthe cylinder bore which in turn draws an infill of the pumping fluidinto the bore. Thereafter, the pump rod is forced into the fluid filledbore displacing a portion of the fluid and producing a pressurizedmovement of the fluid. This type of pump is characterized in that thereis no piston or piston seal required.

U.S. Pat. No. 6,398,514 issued to Smith et al sets forth a DOUBLE-ACTINGROD PUMP having a plurality of rod pumps supported within a driveapparatus which moves the pump rods in opposition to each other withinrespective cylinder bores. The operation reverses during the next cycleof operation allowing the previously filled cylinders to discharge fluidunder pressure while the remaining cylinders are filled. This reversedopposed operation of the plurality of rod pumps produces a virtuallycontinuous flow.

In contrast, rotary pumps are generally characterized as apparatus inwhich input power is coupled to a rotating shaft which in turn iscoupled to a rotating pump mechanism within the pump body. The pump bodydefines a chamber or cavity within which a fluid movement ordisplacement device is rotated by the power input shaft. Perhaps themost pervasive type of rotary pump may be generally described as animpeller, or gear, type pump. In such pumps, a rotor is rotatablysupported within the pump chamber and is driven by the input power shaftto rotate. The rotor in turn supports a plurality of blades which aresized and configured in general correspondence to the interior surfaceof the pump chamber. As the input drive power rotates the rotor, thefluid is carried by the impeller blades within the pump chamber and isdriven from the chamber under pressure. Simultaneously, the outwardmovement of the driven fluid from the chamber produces a draw whichcauses additional fluid to flow into the chamber. The pump operation ismore or less continuous.

Another type of rotary pump is typically referred to as a turbine orvane-type pump. The turbine or vane pump utilizes a housing defining aninterior chamber which is typically cylindrical in shape. A plurality ofstatic blades or vanes are supported in radial disposition upon theinterior surface of the chamber. An armature, also supporting aplurality of vanes or blades is rotatably supported within the chamber.The static blades and the rotating blades of the armature are spaced tofacilitate free rotation of the armature. A source of rotating power iscoupled to the armature to drive the armature usually at high speed.

Still another type of rotary action pump is referred to generally as aperistaltic type pump. Peristaltic pumps are often referred to as “hosepumps” so described because they utilize a elongated flexible tubing orhose within which fluid is disposed. The tubing is typically looped inone or more helical loops within a housing chamber. Inside the helicalloops a rotor is operative to push fluid through the helical hose tubingas the rotor rotates. In most peristaltic pumps the rotor supports aplurality of rollers which are forced against the helical tubing orhose.

U.S. Pat. No. 6,296,460 issued to Smith sets forth a ROTARY CAVITY PUMPhaving a pump housing which supports a plurality of pump segments eachhaving a raised pump cavity enclosed by a resilient diaphragm sealed tothe pump cavity. A compression plate supports a plurality of rollersagainst the pump segments. The compression plate is rotatable withrespect to the pump housing to move the rollers across the pump segmentsdeforming the diaphragms and expelling fluid from the pump segments.Fluid passages couple each pump cavity to a source of fluid and a fluidoutput. As each roller rolls across each diaphragm to expel fluid fromthe pump segment, the resilience of the diaphragm draws the fluid intothe pump segment behind the roller to refill the pump segment.

While the above described prior art pumps have been the subject ofsubstantial refinement and development and have in some measure enjoyedcommercial success, there remains nonetheless a continuing need in theart for ever more improved rotary drive pumps.

SUMMARY OF THE INVENTION

Accordingly, it is a general object of the present invention to providean improved rotary drive pump. It is a more particular object of thepresent invention to provide a highly efficient rotary drive pump whichutilizes displacement pump apparatus and which produces a substantiallyripple free fluid flow.

In accordance with the present invention, there is provided, a rotarydrive linear rod displacement pump comprising: a pump housing; aplurality of displacement pump segments, supported by said pump housing,each including a pump cam follower; a plurality of valve portions,supported by said pump housing, each including a valve cam follower; anda rotor supporting a plurality of roller cams in contact with said valvecam followers and said pump cam followers for actuating said pump assaid rotor rotates.

BRIEF DESCRIPTION OF THE DRAWINGS

The features of the present invention, which are believed to be novel,are set forth with particularity in the appended claims. The invention,together with further objects and advantages thereof, may best beunderstood by reference to the following description taken inconjunction with the accompanying drawings, in the several figures ofwhich like reference numerals identify like elements and in which:

FIG. 1 sets forth a perspective view of a rotary drive linear roddisplacement pump constructed in accordance with the present invention;

FIG. 2 sets forth a perspective view of the present invention rotarydrive linear rod displacement pump having the rotor housing removedtherefrom;

FIG. 3 sets forth a perspective view of the present invention rotarydrive linear rod displacement pump showing the rotor apparatus intransparent view;

FIG. 4 sets forth a perspective view of the present invention rotarydrive linear rod displacement pump having the rotor housing and rotorremoved therefrom;

FIG. 5 sets forth a perspective view of the present invention rotarydrive linear rod displacement pump having the plunger plate and pumpvalve plate removed therefrom;

FIG. 6 sets forth a perspective view of the present invention rotarydrive linear rod displacement pump having the upper seal plate removedtherefrom;

FIG. 7 sets forth a perspective view of the present invention rotarydrive linear rod displacement pump showing the pump segments and valvesegments together with the fluid manifold;

FIG. 8 sets forth a simplified top view the present invention rotarydrive linear rod displacement pump showing the arrangement of the pumpsegments and valve segments;

FIG. 9 sets forth a section view of the present invention rotary drivelinear rod displacement pump taken along section lines 9-9 in FIG. 8;

FIG. 10 sets forth a partial section view of the present inventionrotary drive linear rod displacement pump taken along section lines10-10 in FIG. 8;

FIGS. 11A through 11E set forth sequential section views of the presentinvention rotary drive linear rod displacement pump illustrating theoperational cycle of the pump; and

FIGS. 12A through 12E set forth simplified drawings illustrating therotational operation of the rotor and cams upon the pump segments andvalve segments of the present invention rotary drive linear roddisplacement pump.

DESCRIPTION OF THE PREFERRED EMBODIMENTS OF THE INVENTION

FIG. 1 sets forth a perspective view of a rotary drive linear roddisplacement pump constructed in accordance with the present inventionand generally referenced by numeral 10. Pump 10 is fabricated using aplurality of plates which are joined by a plurality of fasteners toprovide the combined housing for pump 10. It will be apparent to thoseskilled in the art however that the present invention rotary drivelinear rod displacement pump may be fabricated utilizing a differentnumber of plate segments and a different arrangement of plate segmentswithout departing from the spirit and scope of the present invention. Itwill also be apparent to those skilled in the art that, in its preferredform, pump 10 utilizes plates which are formed of appropriate materialsuch as high strength metal or the like. However, once again, it will beunderstood by those skilled in the art that other materials such ascarbon fiber materials or other high strength exotic materials may beutilized without departing from the spirit and scope of the presentinvention. The important aspect in fabricating pump 10 is the combinedstructure of plates forms a pump housing 11 suitable for operating inthe manner described below. Thus, pump housing 11 of pump 10 includes arotor housing 13 joined to a plunger plate 14 which in turn is joined toa pump valve plate 15. Pump housing 11 further includes an upper sealplate 16 joined to a lower seal plate 17 together with a seal supportplate 18. Finally, housing 11 of pump 10 is completed by the attachmentof a fluid plate 19 together with a valve plate 20 and a manifold 21.Pump 10 further includes a generally cylindrical mounting flange 12which defines a plurality of apertures utilized in securing pump 10 to asuitable support surface (not shown).

In further accordance with the present invention, pump 10 includes aninput power shaft 26 which, in the manner described below in greaterdetails, extends through appropriate bores formed in mounting flange 12and rotor housing 13 to support a rotatable rotor (seen in FIG. 9). Asis also better seen in FIG. 11, plates through 21 are secured by aplurality of bolts 24 and 25. As is seen in FIG. 10, upper bolts 24extend downwardly through rotor housing 13 together with plates 14, 15,16, 17 and 18 into fluid plate 19 while lower bolts 25 extend upwardlythrough manifold 21 and valve plate 20 into fluid plate 19. Ofimportance with respect to the present invention is the function bywhich upper bolts 24 and lower bolts 25 (seen in FIG. 11) cooperate tomaintain the security and integrity of pump housing 11. Pump housing 11further supports an input fluid coupling 22 and an output fluid coupling23. The position and orientation of input fluid coupling 22 and outputfluid coupling 23 are set forth in greater detail. However, suffice itto note here that in the normal operation of pump 10, fluid is drawninto pump 10 through input 22 and is expelled outwardly under pressurefrom fluid output 23. In addition, in the anticipated use of the presentinvention pump, input shaft 26 is operatively coupled to a conventionalsource of rotational power (not shown). It will be equally apparent tothose skilled in the art that rotary drive linear rod displacement pump10 may be fabricated in a wide range of sizes to suit particular needsto capacity and flow rates without departing from the spirit and scopeof the present invention.

For purposes of illustration, FIGS. 2 through 7 set forth sequentialperspective views of pump 10 as successive portions are removed from thecombined pump structure in order to facilitate the description andillustration of the structure and operation of the present inventionpump. In addition, the structure in each of FIGS. 2 through 7 has beensimplified to avoid unduly cluttering the figures an allow illustrationof the various system components. More specifically, FIG. 2 sets forthpump housing 11 of pump 10 having rotor housing 13 removed. Thus,plunger plate 14, pump valve plate 15, upper and lower seal plates 16and 17, seal support plate 18, fluid plate 19, valve plate 20 andmanifold 21 remain as previously described. With rotor housing 13removed, input shaft 26 is shown supporting a keeper 32 together with apair of bearings 30 and 31. Also now seen in FIG. 2 with the removal ofrotor housing 13 is rotor 40 secured to input shaft 26 by means setforth below in FIG. 9 in greater detail. Suffice it to note here thatrotor 40 is secured to input shaft 26 and thus rotates therewith. Thus,as input shaft 26 is rotated in the direction indicated by arrow 35,rotor 40 is rotated correspondingly in the direction indicated by arrow34. Plunger plate 14 supports a plurality of pump and cam plungers, suchas plunger 50, each supported within a respective cylindrical sleeveguide such as sleeve guide 60 supporting plunger 50. Rotor 40 furthersupports a plurality of cam plungers such as cam rollers 70, 71 and 72shown in FIG. 2. As will be described below in greater detail, theplurality of cam rollers supported upon rotor 40 are operative to movethe pluralities of plungers supported within the interior of pumphousing 11. In the view shown in FIG. 2, cam rollers 70, 71 and 72 aremoving toward plunger 50 and are operative to depress cam follower 50downwardly within sleeve guide 60. The entire operation of rotor 40 andthe plurality of cam rollers which it supports in actuating theplurality of plungers supported within pump housing 11 is describedbelow in greater detail. However, suffice it to note here that rotor 40is rotated in the direction indicated by arrow 34 with respect to pumphousing 11, the cooperation of cam rollers and plungers within pumpoperates the valve and pump segments shown and described below ingreater detail.

FIG. 3 sets forth the perspective view shown in FIG. 2 in which rotor 40is shown in phantom line depiction in order to illustrate the pluralityof cam followers supported within rotor 40. Thus, as described above,pump 10 includes pump housing 11 supporting plunger plate 14, pump valveplate 15, upper and lower seal plates 16 and 17, seal support plate 18,fluid plate 19, valve plate 20 and manifold 21. As is also describedabove, rotor 40 is joined to input shaft 26 which in turn is sealed by alip seal 32 and is supported by bearings 30 and 31. Plunger plate 14supports a plurality of cam plungers, such as plunger 50, supportedwithin a corresponding plurality of sleeve guides, such as sleeve guide60. Rotor 40 includes an inner hub 41 supporting a plurality of camrollers 83 through 90 (seen in FIG. 12A). Rotor 40 further includes anouter wall 42 which supports a plurality of cam followers 70 through 81(seen in FIG. 13A). As mentioned above, and as is described below ingreater detail, as rotor 40 is rotated by power applied to input shaft26, the pluralities of cam followers supported against inner hub 41 andouter wall 42 are operative upon the plurality of plungers supported byplunger plate 14 to provide the pump operation described below ingreater detail.

FIG. 4 sets forth the perspective view of pump 10 having rotor 40 andshaft 26 together with bearings 30 and 31 and lip seal 32 removedtherefrom. With rotor 40 removed, FIG. 4 shows the positions of thevarious plungers supported within plunger plate 14.

As is described below in greater detail, pump 10 utilizes a plurality ofpump segments operative in combination with a corresponding plurality ofvalve segments. Each portion of pump 10 utilizes the operative pair of apump segment together with a valve segment. Accordingly, and as is seenin FIG. 4, plunger plate 14 supports three dome-shaped plungersoperative upon the valve portions of pump 10. The valve portion plungersare referenced by numerals 50, 51 and 52 and are slidably supportedwithin a corresponding plurality of sleeve guides 60, 61 and 62. As isbetter seen in FIG. 12A, valve plungers 50, 51 and 52 are evenly spacedupon plunger plate 14 and occupy the surface portions of plunger plate14 nearest the outer edge thereof. Also best seen in FIG. 12A, pumpplungers 55, 56 and 57 are equally spaced upon plunger plate 14 and arepositioned inwardly toward the center portion of plunger plate 14.Correspondingly, pump cam followers 55, 56 and 57 are slidably supportedwithin sleeve guides 65, 66 and 67. Returning to FIG. 4, it will beapparent that as rotor 40 (seen in FIG. 3) supporting its plurality ofcam followers (also seen in FIG. 3) is caused to rotate upon the uppersurface of plunger plate 14, plungers 50 through 52 are operative toactuate the valve mechanisms within pump 10. Also seen and alsounderstood, as rotor 40 supporting its plurality of cam followers isrotated upon the surface of plunger plate 14, pump plungers 55, 56 and57 are also operated. By means shown below in greater detail, therotation of rotor 40 upon the plungers causes the valves and pumpsegments within pump 10 to be operated and thereby produce the pumpingaction described below.

FIG. 5 sets forth a perspective view of pump 10 having plunger plate 14and pump valve plate 15 removed therefrom. With plunger plate 14 andpump valve plate 15 removed, a second plurality of guide sleevesoperative to slidably support the pump rods and valve rods is shown.More specifically, sleeve guide 90 supports the valve rod coupled toplunger 50 while sleeve guide 91 supports the valve rod coupled toplunger 51. Similarly, sleeve guide 92 supports the valve rod coupled toplunger 52. Also shown, sleeve guide 95 supports the pump rod coupled toplunger 55 while sleeve guide 96 supports the pump rod coupled toplunger 56 and sleeve guide 97 supports the pump rod coupled to plunger57. FIG. 5 also shows a plurality of return springs operative uponplungers 50 through 52 and plungers 55 through 57.

FIG. 6 shows the perspective view of pump 10 having upper seal plate 16removed therefrom. As described above, pump 10 includes a manifold 21, avalve plate 20, a fluid plate 19, a seal support plate 18 and a lowerseal plate 17. As is also described above, pump 10 includes a pluralityof valve plungers 50, 51 and 52 supported within sleeve guides 60, 61and 62. Also described above, pump 10 includes a plurality of pumpplungers 55, 56 and 57 slidably supported within sleeve guides 65, 66and 67. Further described above, pump 10 includes a plurality of guides90, 91 and 92 supporting the valve rods coupled to valve plungers 50, 51and 52 respectively together with guides 95, 96 and 97 supporting thepump rods coupled to pump plungers 55, 56 and 57. FIG. 6 also shows aplurality of seals 100, 101 and 102 encircling the valve rods coupled tovalve plungers 50, 51 and 52 respectively. FIG. 6 also shows a pluralityof seals 105, 106 and 107 encircling the pump rods coupled to pumpplungers 55, 56 and 57.

FIG. 7 sets forth a perspective view of manifold 21 together with themajor operative components of the present invention pump valve and pumpsegments. As described above, a plurality of valve plungers 50, 51 and52 are supported within sleeve guides 60, 61 and 62 respectively. Aplurality of guides 90, 91 and 92 support the valve rods coupled tovalve plungers 50, 51 and 52. As is also described above, pump 10includes a plurality of pump plungers 55, 56 and 57 supported withinrespective sleeve guides 65, 66 and 67. Sleeve guides 95, 96 and 97further support the pump rods coupled to pump plungers 55, 56 and 57.

Pump 110 further includes a plurality of spring ball check valves 115,116 and 117 operative in combination with each of the pump segments.Pump 10 further includes a plurality of valve seats 110, 111 and 112operative in combination with valve ball ends 120, 121 and 122.

Manifold 21 defines and input fluid channel 27 and an output fluidchannel 28. Fluid channels 27 and 28 are separated by a pair of O-ringseals 47 and 48. An aperture 37 formed within input channel 27 ofmanifold 21 is coupled to input coupling 22. Similarly, an aperture 38is formed within output channel 28 and is coupled to output coupling 23.Thus during normal pump operation, en input flow of fluid flows throughinput coupling 22 through aperture 37 to fill input channel 27.Similarly, during pump operation, fluid under pressure flows outwardlythrough output channel 28 through aperture 38 and output coupler 23.

FIG. 8 sets forth a top view of plunger plate 14 showing the relativepositions of valve plungers 50 through 52 together with pump plungers 55through 57. As mentioned above, valve plungers 50 through 52 aresupported within sleeve guides 60 through 62 respectively while pumpplungers 55 through 57 are supported within respective sleeve guides 65through 67.

FIG. 9 sets forth a section view of pump 10 taken along section lines9-9 in FIG. 8. As described above, pump housing 11 is formed of astacked array of rotor housing 13, plunger plate 14, pump valve plate15, upper and lower seal plates 16 and 17, seal support plate 18, fluidplate 19, valve plate 20 and manifold 21. As is also described above,rotor housing 13 further supports a mounting flange 12 within which ininput shaft 26 is rotatably supported by a pair of bearings 30 and 31.Rotor 40 is joined to input shaft 26 and is rotatable within rotorhousing 13. Rotor 40 further supports a plurality of cam followers inthe manner set forth above in FIG. 3 which includes cam followers 84 and88 as well as cam followers 73 and 79. Pump 10 includes a valve segmentformed by combination of a valve plunger 52 movably supported within asleeve guide 62. The valve segment further includes an elongated valverod 82 extending downwardly from valve plunger 52. Valve rod 82 furthersupports a valve ball 122 at the lower end thereof. A sleeve guide 92 issupported within pump valve plate 15 and provides a guide for valve rod82. A pair of rod seals 102 and 103 encircle valve rod 82 and aresupported within upper seal plate 16 and lower seal plate 17respectively. Fluid plate 19 defines a fluid chamber 125 within which avalve seat 112 is supported. Valve plate 20 defines a fluid chamber 83extending downwardly from valve seat 112. Manifold 21 defines an inputfluid channel 27 (better seen in FIG. 7) which is in communication withfluid passage 83.

The valve segment of pump 10 shown in FIG. 9 is depicted in its valveopen condition characterized by the position of valve ball 122 above andaway from valve seat 112. This open condition allows fluid to flow frominput channel 27 upwardly through fluid passage 83 past valve seat 112into fluid chamber 125. A fluid passage is formed in fluid plate 19(better seen in FIG. 11A) which facilitates fluid coupling to a pumpsegment in the manner shown in FIGS. 11A through 11E below. A pair ofvalve springs are operatively coupled to valve plunger 52 to positionvalve plunger 52 and valve rod 82 in the normally open position shown.The valve segment is moved to a closed valve condition when a camfollower such as cam follower 73 is moved upon plunger 52 forcing valverod 82 and valve ball 122 downwardly. Valve ball 122 moves against valveseat 112 under these circumstances and closes the fluid flow couplingpassage.

FIG. 9 also shows a pump segment supported within housing 11 whichincludes a pump plunger 56 supported within sleeve guide 66 which inturn is supported within plunger plate 14. A pump rod 86 is coupled topump plunger 56 and extends downwardly through a guide 96 which in turnis supported within pump valve plate 15. Pump rod 86 extends downwardlythrough a pair of seals 106 and 108 supported within seal plates 16 and17 respectively. Fluid plate 19 defines a fluid chamber 45 within whicha valve seat 105 is supported. Valve plate 20 defines a fluid chamber 46in communication with fluid chamber 45 through valve seat 105. A valvespring 127 and valve ball 126 are captivated within fluid chamber 46against the underside valve seat 105. The resulting combination of seat105, valve ball 126 and spring 127 forms a check valve operative tolimit fluid transfer to flow from chamber 46 into chamber 45. Fluidchamber 46 is in communication with output channel 28 formed in manifold21. The operation of the pump segment within pump 10 is set forth belowin FIG. 11A through 11E. Suffice it to note here that the pump segmentprovides a rod displacement pump operative when a cam follower exsertsforce against pump plunger 56 forcing pump rod 86 downwardly into fluidchamber 45. The displacement of fluid from chamber 45 overcomes theforce of valve spring 127 moving valve ball 126 away from seat 105 andallowing fluid to flow downwardly through fluid chamber 46 into outputfluid channel 28.

FIG. 10 sets forth a partial section view of a portion of the presentinvention pump taken along section lines 10-10 in FIG. 8. Of importanceto note in FIG. 10 is the extension of upper bolt 24 downwardly to bereceived within threaded bore 34 formed in fluid plate 19. Similarly,lower bolt 25 extends upwardly to be received within the lower portionof threaded bore 34 in fluid plate 19. The cooperation of upper bolts 24and lower bolts 25 each threadably coupled within threaded bore 34secures the integrity of housing 11.

FIG. 11A through 11E set forth sequential views of a section view of thepresent invention pump taken along section lines 11-11 in FIG. 8. Whilethe section views shown in FIGS. 11A through 11E are somewhat simplifiedto aid in discussion, they provide sequential views showing theoperation of the cooperating pump segment and valve segment of thepresent invention rotary drive linear rod displacement pump. Thus withconcurrent reference to FIGS. 11A through 11E, plunger plate 14, pumpvalve plate 15, upper seal plate 16, lower seal plate 17, seal supportplate 18, fluid plate 19, valve plate 20 and manifold 21 are joinedtogether in the above-described manner. Plunger plate 14 supports avalve plunger 50 received within a sleeve guide 60. Plunger plate 14further supports a guide 95 while upper seal plate 16 supports a seal105. Lower seal plate 17 supports a seal 109. Fluid plate 19 furtherdefines a fluid chamber 119 within which a valve seat 130 is supported.Valve plate 20 defines a fluid chamber 133 within which a valve ball 131and a spring 132 are captivated. Manifold 21 defines an output fluidchannel 28 (better seen in FIG. 7) which is in communication with fluidchamber 133. A pump rod 88 is coupled to pump plunger 55 and extendsdownwardly through guide 95, seal 105 and seal 109. The lower end ofpump rod 88 extends into fluid chamber 119. A return spring 89 isoperatively coupled between pump rod 88 and cam follower 55 to urge pumprod 88 and pump cam follower 55 upwardly. The check valve formed by thecombination of ball 131 and spring 132 forms a normally closed valve inwhich ball 131 is urged against seat 130.

Pump valve plate 15 supports a sleeve guide 90. Upper seal plate 16supports a seal 100 while lower seal plate 17 supports a seal 104. Fluidplate 19 defines a fluid chamber 136 within which a valve seat 110 issupported. Valve plate 20 defines a fluid chamber 137 which is incommunication with input fluid channel 27 formed in manifold 21. Anelongated valve rod 114 is operatively coupled to valve plunger 50 andextends downwardly through guide 90, seal 100 and seal 104. The lowerend of valve rod 114 extends further into fluid chamber 136 and supportsa valve ball 120 at its lower end. Fluid plate 19 supports a valve seat110. Valve plate 20 defines a fluid chamber 137 which is in fluidcommunication with chamber 136 and input fluid channel 27 (seen in FIG.7). A spring 118 is operatively coupled between pump valve plate 15 andvalve rod 114 to urge valve rod 114 upwardly against valve cam follower50 which in turn raises valve plunger 50.

With specific reference to FIG. 11A, pump 10 assumes the initialposition in which both pump rod 88 and valve rod 114 have been forceddownwardly to their lowered positions. It should be noted that theposition shown in FIG. 11A corresponds to the positions for the camfollowers shown in FIG. 12A in which plungers 55 and 50 are both forceddownwardly by cam followers 73 and 83 respectively. Returning to FIG.11A, with pump rod 88 in its downward position, the fluid volume withinchamber 119 is at its minimum volume. Correspondingly, the downwardposition of valve rod 114 forces valve ball 120 against seat 110 closingchamber 136 and isolating it from chamber 137 and input fluid channel127. Thereafter, as rotor 40 (seen in FIG. 12A) rotates to move camfollowers 73 and 83 away from valve plunger 50 and pump plunger 55,spring 89 moves pump rod 88 upwardly while spring 118 moves valve rod114 upwardly. The upward movement of valve rod 114 withdraws valve ball120 from seat 110 allowing fluid coupling between passages 136 and 137into input fluid channel 27. Concurrently, the upward movement of pumprod 88 provided by spring 89 increases the fluid volume of fluid chamber119 which in turn draws fluid upwardly from input fluid channel 27 intofluid chamber 137 and further upwardly through fluid chamber 136. Fluidthen flows through fluid passage 135 into fluid chamber 119 fillingfluid chamber 119 as pump rod 88 rises to the intermediate positionshown in FIG. 11B.

FIG. 11B shows the configuration of pump and valve segments within pump10 at an intermediate point as pump rod 88 and valve rod 114 continue torise. This configuration corresponds to FIG. 12B which shows camfollowers 73 and 83 moving off of plungers 50 and 55 respectively.Returning to FIG. 11B, the continued upward movement of pump rod 88continues the expansion of fluid chamber 119 which in turn allowscontinued fluid draw upwardly from input channel 27 through fluidchambers 137 and 136 and ultimately into fluid chamber 119 through fluidpassage 135.

FIG. 11C shows the pump configuration as pump rod 88 and valve rod 114assume their upper most positions. This configuration in turncorresponds to FIG. 12C in which cam follower 73 has moved away fromplunger 50 and cam follower 83 has moved away from plunger 55. In theconfiguration shown in FIG. 11C, fluid chamber 119 is filled with fluiddrawn upwardly from input fluid channel 27. It will be noted in FIG. 11Cthat ball 131 is forced against valve seat 130 closing the valve at thebottom end of fluid chamber 119. It will also be noted that valve ball120 is withdrawn from valve seat 110. Thus, the entire fluid chamberarrangement is at this point filled with fluid drawn upwardly by theupward movement of pump rod 88.

FIG. 11D shows the configuration of the present invention pump as rotor40 continues rotating to the position shown in FIG. 12D. As set forththerein, cam follower 72 has moved upon plunger 50 which again forcedcam rod 114 downwardly forcing valve ball 120 against valve seat 110.This closure isolates fluid chamber 136 from fluid chamber 137 and inputchannel 27. As the rotation of rotor 40 continues to the position shownin FIG. 12E, cam follower 89 moves upon pump plunger 55 driving pump rod88 downwardly into fluid chamber 119. The insertion of the lower end ofpump rod 88 into filled fluid chamber 119 creates a displacement offluid within chamber 119. This in turn produces a fluid pressure withinfluid chamber 119 causing the pump to assume the configuration shown inFIG. 11E.

FIG. 11E shows the configuration of pump 10 as pump plunger 55 and pumprod 88 are driven downwardly by the force of cam follower 89 (seen inFIG. 12E). This fluid pressure forces valve ball 131 away from valveseat 130 opening the check valve and forcing fluid under pressuredownwardly through fluid chamber 133 into output fluid channel 28 withinmanifold 21. This pressurized fluid flow into output channel 28 in turnproduces an outward fluid flow from the pump. As rotor 40 continues torotate, cam follower 89 moves across and away from pump plunger 55 andthe system assumes the configuration represented by FIGS. 11A and 12A.In the absence of fluid pressure, valve ball 131 is forced upwardlyagainst seat 130 by spring 132 returning the entire system to theconfiguration shown in FIG. 11A which results from the rotor positionshown in FIG. 12A.

FIGS. 12A through 12E set forth sequential top views of pump 10 havingrotor housing 13 removed. The sequential views of FIGS. 12A through 12Eprovide somewhat simplified views to best facilitate an understanding ofthe operation of the present invention pump. Accordingly, certainstructural features of pump 10 are omitted from the figures such asupper bolts 24. Furthermore, FIGS. 12A through 12E show the positions ofrotor 40 which correspond to the sequential pump section views shown inFIGS. 11A through 11E.

Accordingly and with concurrent reference to FIGS. 12A through 12E, pump10 includes housing 11 having plunger plate 14 thereon. Plunger plate 14supports, sleeve guides 60 through 62 and 65 through 67. Sleeve guides60 through 62 support valve cam followers 50 through 52 while sleeveguides 65 through 67 support pump cam followers 55 through 57.

Rotor 40 is driven by input shaft 26 and includes an inner hub 41 and anouter wall 42. Hub 41 supports a plurality of cam followers 83 through90 in a radially equally spaced array. Cam followers 84, 86, 88 and 90are positioned higher upon hub 41 and are solely operative to limit theupward travel of pump plungers 55, 56 and 57. Cam followers 83, 85, 87and 89 are positioned at lower positions on hub 41 to interact with pumpplungers 55, 56 and 57. Cam followers 70 through 81 are supported bywall 42 and are arranged in groups of three in an equally radiallyspaced array. Cam followers 70 through 81 interact with vale plungers50, 51 and 52 as rotor 40 is rotated.

With specific reference to FIG. 12A, rotor 40 is shown at the start of apump cycle for the portion of pump 10 formed by the combination of thepump segment driven by pump plunger 50 and valve plunger 55. It shouldbe noted that the remaining portions of pump 10 formed by the pump andvalve segments driven by pump plungers 56 and 57 together with valve camplungers 51 and 52 operate in the same manner as described below. Ineffect, pump 10 includes three pump portions simultaneously driven byrotor 40. It will also be noted that these three pump portions operatein interleaved sequences due to the radial arrangement of the camfollowers on rotor 40. This provides interleaved pump cycles whichminimizes, and virtually eliminates pressure ripple in the pump output.

In the position shown in FIG. 12A, cam follower 73 is forcing valveplunger 50 downwardly while cam follower 83 is forcing pump plungerdownwardly causing the valve and pump segments to assume the positionsin FIG. 11A. Thus, both valve rod 114 and pump rod 88 are at theirlowest positions.

As rotor 40 rotates in the direction indicated by arrow 140, rotor 40reaches the position shown in FIG. 12B. Cam followers 73 and 83 aremoving away from the high points of valve plunger 50 and pump plunger55. This allows valve rod 114 and pump rod 88 to begin rising to thepositions shown in FIG. 11B. This in turn opens the valve and drawsfluid into the pump segment.

As rotor 40 continues to rotate, it reaches the position shown in FIG.12C in which valve plunger 50 is free of any cam follower and rises tothe full height shown in FIG. 11C. Correspondingly, raised cam follower90 limits the upward travel of the pump plunger to the maximum travelposition shown in FIG. 11C. The pump potion is at this point fullyfilled.

As rotor 40 rotates to the position shown in FIG. 12D, cam follower 72forces valve plunger 50 downwardly to the position shown in FIG. 11Dwhich closes the pump valve as shown therein. The pump segment remainsthe same, that is, filled with fluid and pump rod 88 raised.

As rotor 40 continues to rotate, it reaches the position shown in FIG.12E. At this point, cam followers 72, 71 and 70 have continued todepress valve plunger 50 maintaining the valve in the closed positionshown in FIG. 11E. However, during the rotation of rotor 40 from theposition shown in FIG. 12D to that shown in FIG. 12E, cam follower 89depresses pump plunger 55 which drives pump rod 88 downwardly as shownin FIG. 11E. This provides the displacement pumping action of thepresent invention pump.

This cycle is repeated for each of the pump portions as rotor 40 isdriven by a power source coupled to input shaft 26. It will be apparentto those skilled in the art that while the embodiments set forth hereinshow a pump having three pump portions in combination, Pumps havingdifferent numbers of pump potions may be utilized without departing fromthe spirit and scope of the present invention.

While particular embodiments of the invention have been shown anddescribed, it will be obvious to those skilled in the art that changesand modifications may be made without departing from the invention inits broader aspects. Therefore, the aim in the appended claims is tocover all such changes and modifications as fall within the true spiritand scope of the invention.

1. A rotary drive linear rod displacement pump comprising: a pumphousing; a plurality of displacement pump segments, supported by saidpump housing, each including a pump plunger; a plurality of valveportions, supported by said pump housing, each including a valveplunger; and a rotor supporting a plurality of cam followers in contactwith said valve plungers and said pump plungers for actuating said pumpas said rotor rotates.
 2. A rotary drive continuous flow linear roddisplacement pump comprising: a pump housing; a plurality of linear roddisplacement pump segments, supported by said pump housing and eachincluding a pump plunger for actuating each of said linear roddisplacement pump segments; a plurality of valve segments, supported bysaid pump housing, each including a valve plunger for actuating each ofsaid valve segments; and a rotor, supported for rotation with respect tosaid pump housing, supporting a plurality of cam followers actuatingsaid linear rod displacement pump segments and said valve segments assaid rotor is caused to rotate.
 3. The rotary drive continuous flowlinear rod displacement pump set forth in claim 2 wherein each of saidlinear rod displacement pump segments include: a fluid chamber; and apump rod movable within said fluid chamber between a withdrawn positionallowing fluid to be received into said fluid chamber and an insertedposition displacing fluid and expelling it from said fluid camber. 4.The rotary drive continuous flow linear rod displacement pump set forthin claim 3 wherein said pump housing includes a fluid manifold defininga fluid input accumulating channel in fluid communication with saidplurality of valve segments and a fluid output accumulating channel influid communication with said plurality of linear rod displacement pumpsegments.
 5. The rotary drive continuous flow linear rod displacementpump set forth in claim 4 wherein said fluid input accumulating channelincludes a fluid input for coupling to a supply of fluid and whereinsaid fluid output accumulating channel includes a fluid output fordischarging fluid from said rotary drive continuous flow linear roddisplacement pump.
 6. The rotary drive continuous flow linear roddisplacement pump set forth in claim 5 wherein said plurality of linearrod displacement pump segments and said plurality of valve segments aresupported by said pump housing in a radially spaced arrangement wherebyeach of said plurality of linear rod displacement pump segments and saidplurality of valve segments are actuated sequentially as said rotor iscaused to rotate.
 7. The rotary drive continuous flow linear roddisplacement pump set forth in claim 6 wherein said plurality of linearrod displacement pump segments and said plurality of valve segments areoperatively coupled in associated pairs in which fluid flow into saidfluid chamber of each linear rod displacement pump segment flows throughits associated valve segment.
 8. A rotary drive linear rod displacementpump comprising: a pump housing having a plunger plate supporting aplurality of pump plungers movable with respect to said plunger plateand a plurality of valve plungers movable with respect to said plungerplate; a plurality of displacement pump segments, supported by said pumphousing, each actuated by one of said pump plungers; a plurality ofvalve portions, supported by said pump housing, each actuated by one ofsaid valve plungers; and a rotor supporting a plurality of cam followerscontacting and depressing said valve plungers and said pump plungers assaid rotor is caused to rotate.
 9. The rotary drive continuous flowlinear rod displacement pump set forth in claim 8 wherein said pluralityof linear rod displacement pump segments and said plurality of valvesegments are operatively coupled in associated pairs in which fluid flowinto said fluid chamber of each linear rod displacement pump segmentflows through its associated valve segment.
 10. The rotary drive linearrod displacement pump set forth in claim 9 wherein said displacementpump segments each include: a fluid chamber formed in said housing; apump rod, coupled to a pump plunger, supported for movement between awithdrawn position and an inserted position relative to said fluidchamber; and a discharge output; and a pump rod spring urging said pumprod and its coupled pump plunger toward said withdrawn position, saidpump plunger moving said pump rod from said withdrawn position to saidinserted position as said cam followers contact said pump plunger duringrotation of said rotor.
 11. The rotary drive linear rod displacementpump set forth in claim 10 wherein said valve segments each include: avalve rod supported within said pump housing coupled to a valve plunger;a valve closure moveable between an open condition allowing fluid toflow into said fluid chamber and a closed condition preventing fluidflow from said fluid chamber; and a valve rod spring urging said valverod and its coupled valve plunger toward said open condition; said valveplunger moving said valve rod from said open condition to said closedcondition as said cam followers contact said valve plunger duringrotation of said rotor.
 12. The rotary drive continuous flow linear roddisplacement pump set forth in claim 11 wherein said plurality ofdisplacement pump segments and said plurality of valve segments aresupported by said pump housing in a radially spaced arrangement wherebyeach of said plurality of rod displacement pump segments and saidplurality of valve segments are actuated sequentially as said rotor iscaused to rotate.